WO2000073664A1 - Dispositif de regulation du debit nominal d'une pompe et dispositif a soupape - Google Patents

Dispositif de regulation du debit nominal d'une pompe et dispositif a soupape Download PDF

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Publication number
WO2000073664A1
WO2000073664A1 PCT/JP2000/003386 JP0003386W WO0073664A1 WO 2000073664 A1 WO2000073664 A1 WO 2000073664A1 JP 0003386 W JP0003386 W JP 0003386W WO 0073664 A1 WO0073664 A1 WO 0073664A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
port
throttle
pump
spool
Prior art date
Application number
PCT/JP2000/003386
Other languages
English (en)
Japanese (ja)
Inventor
Yusaku Nozawa
Mitsuhisa Tougasaki
Yoshizumi Nishimura
Kinya Takahashi
Original Assignee
Hitachi Construction Machinery Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Construction Machinery Co., Ltd. filed Critical Hitachi Construction Machinery Co., Ltd.
Priority to EP00929873A priority Critical patent/EP1099856A1/fr
Priority to KR10-2003-7002113A priority patent/KR20030019921A/ko
Priority to KR1020007014513A priority patent/KR20010053054A/ko
Priority to US09/744,308 priority patent/US6422009B1/en
Priority to JP2001500127A priority patent/JP3756814B2/ja
Publication of WO2000073664A1 publication Critical patent/WO2000073664A1/fr

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2703—Flow rate responsive
    • Y10T137/2705—Pressure differential

Definitions

  • the present invention relates to a pump for a hydraulic drive device including a load sensing system that controls the capacity of a hydraulic pump so as to maintain a differential pressure between a discharge pressure of a hydraulic pump and a maximum load pressure of a plurality of actuators at a set differential pressure.
  • the present invention relates to a displacement control device, and more particularly to a pump displacement control device that controls the displacement of a hydraulic pump by linking the displacement to an engine speed, and a valve device used in the pump displacement control device.
  • One of the hydraulic systems that controls each actuator of the hydraulic excavator detects the load pressure of each actuator and determines the sum of the highest pressure among the load pressures and the set differential pressure.
  • the set differential pressure (hereinafter, appropriately referred to as LS set differential pressure) is normally set to a certain value (for example, 15 bar) by an urging means, for example, a panel.
  • a fixed displacement bomb provided as a hydraulic pressure source of a pilot hydraulic circuit for operating devices such as a hydraulic remote control valve group is discharged.
  • a throttle is arranged in the passage, the upstream pressure of this throttle is detected as a signal pressure Pc, and this signal pressure Pc is the same as the pressure receiving part of the load pressure P1 s of the single sensing valve via the signal oil passage. It is guided to the pressure receiving part on the side. Since the upstream pressure of the throttle changes according to the rotation speed of the fixed displacement pump, the detected signal pressure P c is equal to the rotation speed. You will have the degree information.
  • the pump displacement control device described in Japanese Patent Application Laid-Open No. Hei 5-9991 26 discloses a servo piston that tilts a swash plate of a variable displacement hydraulic cylinder, a discharge pressure Ps of a hydraulic pump, and a hydraulic pump.
  • the pump discharge pressure is supplied to the servo piston by the pressure difference ⁇ P LS from the load pressure P LS of the actuator that is driven by the actuator, and the pressure difference ⁇ P LS is maintained at the set value ⁇ P LS ref.
  • a rotation control device is also known in Japanese Patent Application Laid-Open No. Hei 5-9991 26 .
  • the capacity of the hydraulic pump does not change even if the engine speed is reduced, so the supply flow rate to the actuator is reduced. Does not change, and the speed of the night is not linked to the engine speed and cannot be reduced.
  • the working speed can be adjusted by adjusting the opening of the throttle of the flow control valve, but for this purpose, the operating position of the operating lever that adjusts the opening of the throttle of the flow control valve must be maintained in the middle range. In order to improve the fine operability, even if the operation lever is kept at the full position, if the engine speed is reduced, the maximum speed of the actuator (the maximum supply flow rate to the actuator) is reduced accordingly. It is desirable that the maximum working speed can be adjusted.
  • the differential pressure set for the load sensing valve detects the upstream pressure of the throttle provided in the discharge passage of the fixed pump as the signal pressure Pc. This signal pressure is given by P c.
  • the signal pressure (upstream pressure of the throttle) Pc is reduced, so the set differential pressure of the load-sensing valve is also reduced, the capacity of the hydraulic pump is reduced, and the working speed of the actuator is reduced. Slows down. Therefore, the working speed can be adjusted by controlling the capacity of the hydraulic pump linked to the engine speed.
  • the pilot hydraulic circuit is for generating a signal pressure for operating devices such as a hydraulic remote control valve group, and the pressure downstream of the throttle for detecting the engine speed is a relief valve for setting the pilot-secondary pressure.
  • the set pressure is Pa and the pressure loss of the throttle for detecting the engine rotational speed is Pb
  • the fixed pump discharges 35 liters / min (the set pressure Pa is Assuming that the pressure is maintained at 45 bar even if consumed, and the pressure loss Pb at the throttle for detecting the engine speed is 15 bar, the upstream pressure Pc of the throttle is 60 bar.
  • the equivalent pressure of the spring of the conventional general load sensing system in which the set differential pressure of the load sensing valve is given by a panel is, for example, about 15 bar, which is described in Japanese Utility Model Laid-Open No. 2-149881.
  • the set value APLSref of the tilt control device is changed not by the upstream pressure Pc of the throttle for detecting the engine rotational speed but by the differential pressure ⁇ p across the throttle. ing.
  • the pressure difference ⁇ P p across the throttle corresponds to the pressure loss Pb of the throttle, and is 15 bar in the above example. This is the same as the equivalent pressure 15 bar of the panel of a general road sensing system. Therefore, when the pressure difference ⁇ P p across the throttle is used instead of the upstream pressure P c of the throttle, the pressure difference ⁇ P p can be directly applied to the pressure receiving portion of the mouth sensing valve. It is possible to avoid complication of the structure. However, this conventional technique has the following problems.
  • the change range of the rotation speed of the engine is 1000 to 2000 rpm.
  • the differential pressure across the throttle for detecting the engine speed is 15 bar as described above
  • the engine rotation speed is 100 rpm
  • the differential pressure across the throttle is 7.5 bar
  • the change in the engine speed is between 100 and 200 rpm. It varies between 7.5 and 15 bar.
  • the set differential pressure changes in the range of 7.5 to 15 bar for the engine speed change range of 100 to 200 rpm, and the set differential pressure is 7.5. It cannot be reduced below bar. Therefore, the capacity of the hydraulic pump could not be reduced to a certain value or more in the idle rotation region where the amount of work was small, and there was a limit in improving the fine operability, and the fuel consumption could not be reduced.
  • An object of the present invention is to make it possible to use the pressure linked to the engine rotational speed as it is as the set differential pressure of the load sensing valve, thereby avoiding the complexity of the structure of the load sensing valve, and in an idle rotation region where the amount of work is small.
  • An object of the present invention is to provide a pump displacement control device capable of improving the fine operability by reducing the displacement of a hydraulic pump and reducing fuel consumption, and a valve device used for the pump displacement control device.
  • the present invention provides an engine and a variable displacement hydraulic pressure which is driven to rotate by the engine and supplies pressure oil to a plurality of actuators via respective flow control valves.
  • a hydraulic drive device having a pump, and controls a capacity of the hydraulic pump so as to maintain a differential pressure between a discharge pressure of the hydraulic pump and a maximum load pressure of the plurality of actuators at a target differential pressure.
  • a pump displacement control device that detects a change in the rotational speed of the engine based on a change in the differential pressure across the throttle and changes the target differential pressure to control the displacement of the variable displacement hydraulic pump.
  • a differential pressure detecting unit that detects a differential pressure across the throttle and outputs a pressure lower than the differential pressure by a predetermined value as a signal pressure, and sets a target differential pressure of the load sensing valve based on the signal pressure. It shall be.
  • the pressure (signal pressure) lower than the differential pressure across the throttle, which is the output of the differential pressure detecting means, by a predetermined value has information on the engine rotational speed. Control the displacement of the hydraulic pump and detect the differential pressure across the throttle rather than the upstream pressure as a signal pressure linked to the engine speed, so that the signal pressure is modulated on the load sensing valve side
  • the target differential pressure can be set without the need, and the structure of the load sensing valve can be simplified.
  • the pressure that is lower by a predetermined value than the differential pressure across the throttle which is the output of the differential pressure detection means at the rated engine speed, is the same as the differential pressure across the conventional throttle that uses the differential pressure across the throttle as it is. If the opening area of the throttle is set so that the pressure difference before and after the throttle with respect to the engine speed becomes larger than before, the output of the differential pressure detecting means in the idle rotation region will be smaller than that of the conventional throttle.
  • the pressure difference is smaller than the front-rear pressure difference, and the capacity of the hydraulic pump can be reduced in the idle rotation region where the amount of work is small, improving the fine operability and reducing the fuel consumption.
  • the differential pressure detecting means is configured to guide pressure on the upstream side of the throttle and operate to connect its output side to the upstream side of the throttle.
  • a pressure receiving section a second pressure receiving section that operates to connect the pressure on the downstream side of the restrictor and connects its own output side to the tank, and a pressure receiving section on its own output side, and outputs the pressure on its own output side
  • a panel for setting its predetermined value by operating a third pressure receiving portion that operates to connect the tank to the tank, and a panel that operates to connect its output side to the tank.
  • the differential pressure detecting means operates to reduce the output by the above-mentioned predetermined value which is the set value of the panel with respect to the differential pressure before and after the throttle, and outputs a pressure lower by a predetermined value than the differential pressure before and after the throttle.
  • the differential pressure detecting means is configured as a valve device integrated with the throttle, and the valve device is connected to a discharge path of the fixed displacement hydraulic pump.
  • a pump port, a tank port connected to a tank, a circuit port connected to a pilot hydraulic circuit operated by discharge oil of the fixed capacity hydraulic pump, a load sensing boat connected to the load sensing valve, and the pump A throttle passage that constantly communicates with the boat and the circuit port, functions as the throttle, a first notch that controls communication between the pump port and the load sensing port, and controls communication between the mouth sensing boat and the tank port.
  • a spool having a second notch formed therein, and selectively opening the first notch and the second notch; And a spool urging means for generating a pressure lower than the differential pressure across the throttle by a predetermined value at the load sensing port.
  • the differential pressure detecting means By thus configuring the differential pressure detecting means as a valve device integrated with the throttle, a complex of the throttle and the differential pressure detecting valve can be realized with a simplified configuration.
  • the throttle passage formed in the spool has a throttle hole that opens in a radial direction of the spool.
  • the spool urging means is configured to urge the spool in the opening direction of the first notch by guiding the pressure of the pump port.
  • a pressure receiving portion, a pressure of the circuit port is guided, a second pressure receiving portion formed to urge the spool in a direction of opening the second notch, and a pressure of the closed sensing port are guided,
  • the spool urging means selectively opens the first notch and the second notch, and generates a pressure lower than the differential pressure across the throttle by a predetermined value in the load sensing port.
  • the present invention provides a fixed displacement hydraulic pump that is provided with a variable displacement hydraulic pump in a discharge path of a fixed displacement hydraulic pump that is rotationally driven by an engine.
  • a valve device that outputs a corresponding signal pressure and sets a target differential pressure of a single sensing valve provided in the variable displacement hydraulic pump.
  • the valve device is connected to a discharge path of the fixed displacement hydraulic pump.
  • a pump port a tank port connected to a tank, a circuit port connected to a pilot hydraulic circuit operated by discharge oil of the fixed displacement hydraulic pump, a load sensing port outputting the signal pressure, and the pump
  • a throttle passage which constantly communicates a port with the circuit boat and functions as the throttle; a first knob which controls communication between the pump port and the load sensing port; And a spool formed with a second notch for controlling communication between the load sensing boat and the tank boat, and selectively controlling the first notch and the second notch.
  • a spool urging means for opening the load sensing port to generate a pressure lower than the differential pressure across the throttle by a predetermined value at the load sensing port.
  • the above (1) 1) and 2) can be obtained.
  • the complexity of the structure of the load sensing valve can be avoided, and the capacity of the hydraulic pump can be reduced in the idle rotation region where the amount of work is small, so that the fine operability can be improved and the fuel consumption can be reduced.
  • the throttle passage formed in the spool has a throttle hole that opens in a radial direction of the spool.
  • the spool urging means is configured to urge the spool in the opening direction of the first notch by guiding the pressure of the pump port.
  • a pressure receiving portion, a pressure of the circuit port is guided, a second pressure receiving portion formed to urge the spool in a direction of opening the second notch, and a pressure of the port-sensing port are guided;
  • the spool urging means selectively opens the first notch and the second notch, and generates a pressure lower than the differential pressure across the throttle by a predetermined value at the load sensing port.
  • FIG. 1 is a circuit diagram showing a pump displacement control device according to one embodiment of the present invention.
  • FIG. 2 is a diagram showing output characteristics of a differential pressure detecting valve in the pump displacement control device shown in FIG.
  • FIG. 3 is a circuit diagram of a valve device in which the fixed throttle and the differential pressure detection valve shown in FIG. 1 are integrated.
  • 4A is a cross-sectional view showing the structure of the valve device shown in FIG. 3, and
  • FIG. 4B is a diagram showing each pressure receiving portion of the differential pressure detecting valve.
  • reference numeral 1 denotes a variable displacement hydraulic pump.
  • the hydraulic pump 1 has a displacement adjusting member 2 and is driven to rotate by an engine 9.
  • the discharge path 1a of the hydraulic pump 1 is connected to the directional control valves 6, 6, and the discharge oil from the hydraulic pump 1 is supplied to the directional control valves 6, 6.
  • the directional control valves 6, 6 have meter-in flow control throttles 6a, 6a, and the pressure oil passing through the flow control throttles 6a, 6a has the same differential pressure across the flow control throttles 6a, 6a.
  • the fluid flows into the actuator 21 and 21 through the hold check valves 20 and 20.
  • the maximum load pressure P 1 s is detected between the pressure compensating valves 7, 7 and the hold check valves 20, 20 via the high pressure selection valve 8, and the maximum load pressure P 1 s is determined by the pressure compensating valves 7, 7. And controls the differential pressure across the flow control restrictors 6a and 6a as described above.
  • An unload valve 2 2 is connected to the discharge path 1 a of the hydraulic pump 1, and the maximum load pressure P 1 s detected by the high-pressure selection valve 8 is also guided to the unload valve 22 to discharge the hydraulic pump 1. Specifies the maximum value of the differential pressure between the pressure and the maximum load pressure P 1 s.
  • reference numeral 25 denotes a pump displacement control device of the present embodiment.
  • the pump displacement control device 25 is a large-diameter piston 3 that operates the displacement adjusting member 2 of the hydraulic pump 1 in the small displacement direction.
  • a small-diameter piston 4 for operating the capacity adjusting member 2 in the large-capacity direction, and a load sensing valve 5.
  • the pressure receiving chamber 3 a of the large-diameter biston 3 is connected to the tank T or the hydraulic pump 1 by the load sensing valve 5.
  • the connection to the discharge path 1a is controlled, and the pressure receiving chamber 4a of the small diameter biston 4 is connected to the discharge path 1a.
  • the load sensing valve 5 has a pressure receiving portion 5a on the side that operates to connect the discharge path 1a to the pressure receiving portion 3a of the large-diameter piston 3, and connects the tank T to the pressure receiving portion 3a. It has pressure receiving parts 5b and 5c on the operating side.
  • the pressure P i (pump discharge pressure) of the discharge path 1a is guided to the pressure receiving part 5a, and the high pressure selection valve 8 is applied to the pressure receiving part 5b.
  • the last detected High load pressure P 1 s is induced via signal path 26, and signal pressure P c (described later) is induced in pressure receiving section 5 c.
  • a drain portion 5d is further provided on a side that operates so as to connect the discharge passage 1a of the load sensing valve 5 to the pressure receiving portion 3a of the large diameter piston 3.
  • the load sensing valve 5 operates in balance with the pressure P i of the discharge path 1 a, the maximum load pressure P 1 s, and the signal pressure P c, and the differential pressure (P i — P 1 s) is changed to the signal pressure P c If it is larger, the load sensing valve 5 is moved to the right in the figure, and the pressure oil in the discharge path 1a is led to the pressure receiving chamber 3a, and the difference between the pressure Pi in the discharge path 1a and the maximum load pressure P1s The capacity (tilt angle) of the hydraulic pump 1 is reduced until the pressure becomes equal to the signal pressure Pc.
  • the pressure sensing valve 5 is at the position shown in the drawing, and the pressure in the pressure receiving chamber 3a is reduced to the tank T. And the capacity (tilt angle) of the hydraulic pump 1 is increased by the force of the small diameter piston 4.
  • the differential pressure across the flow control throttles 6a, 6a is kept constant, and at the same time, by the operation of the pressure compensating valves 7, 7, each of the actuators 21 1, 2 Even if there is a difference in the load pressure of 1, the differential pressure across the flow control throttles 6a and 6a becomes the same value for all factories, and passes according to the opening area ratio of the flow control throttles 6a and 6a.
  • the flow rate is controlled, and it is possible to perform combined operation of 21 and 21 with a negative pressure difference.
  • the pump displacement control device 25 is a fixed displacement hydraulic pump (hereinafter abbreviated as a fixed pump) that is rotationally driven by the same engine 9 as the hydraulic pump 1. 1 and 2, a differential pressure detection valve 31 that detects the differential pressure across the fixed throttle 1 2 and outputs a pressure lower than the differential pressure by a predetermined value, and an output of the differential pressure detection valve 3 1 And a signal oil passage 14 for guiding the pressure sensing portion 5 c of the load sensing valve 5.
  • a fixed displacement hydraulic pump hereinafter abbreviated as a fixed pump
  • a differential pressure detection valve 31 that detects the differential pressure across the fixed throttle 1 2 and outputs a pressure lower than the differential pressure by a predetermined value
  • an output of the differential pressure detection valve 3 1 And a signal oil passage 14 for guiding the pressure sensing portion 5 c of the load sensing valve 5.
  • the fixed pump 11 is originally used as a hydraulic power source for a pilot hydraulic circuit 41 that operates devices such as a hydraulic remote control valve group 40.
  • the rotation speed of the engine 9 is 200 It has a capacity to obtain a discharge oil volume of about 351 / min at rpm.
  • the pilot hydraulic circuit 41 is provided with a relief valve 13. The relief valve 13 sets the pressure downstream of the fixed throttle 12 of the pilot hydraulic circuit 41 to a constant pressure of, for example, about 45 bar. Have been.
  • the fixed throttle 12 has a difference of, for example, about 1513 & 1 ", which is about 25 ar.
  • the opening area is set so that the pressure (resistance) can be obtained
  • the differential pressure detection valve 31 has a pressure receiving part 31 on the side that operates so as to connect the upstream side of the constant differential pressure restrictor valve 30 to its own output side. a and a pressure receiving portion 31b, 31c on the side that operates to connect the tank T to its own output side, and the pressure receiving portion 31a is upstream of the fixed throttle 12 via an oil passage 32. Of the fixed throttle 12 via the oil passage 33 to the pressure receiving portion 31b via the oil passage 33, and the pressure P 1 via the oil passage 34 to the pressure receiving portion 31c.
  • the differential pressure detection valve 31 has a spring 3 I on its side that operates to connect the tank T to its own output side. d
  • the oil passage 34 is provided with a throttle 35 that suppresses a rapid change in hydraulic pressure acting on the pressure receiving section 1.
  • the differential pressure detecting valve 31 configured in this manner has a pressure P 1 on the upstream side of the fixed throttle 12, a pressure P 2 on the downstream side of the fixed throttle 12, its own output pressure P c, and a panel 3 Id. Operates in proportion to the force's hydraulic pressure conversion value P k,
  • the balance condition is satisfied when Pc that satisfies is formed on the output side of the differential pressure detection valve 31. That is, the differential pressure detecting valve 31 outputs a pressure Pc lower by Pk than the differential pressure P1—P2 across the fixed throttle 12.
  • the panel 31 d has the above Pk of, for example, 1 O It is set to be about bar.
  • the differential pressure detection valve 31 is provided with the panel 31 d as described above, and the differential pressure across the fixed throttle 12 A pressure Pc that is lower than (P1—P2) by the set value Pk on the panel 31 is output.
  • FIG. 2 shows the output characteristics of such a differential pressure detecting valve 31 in comparison with the conventional one.
  • the solid line A indicates the characteristic of the differential pressure detecting valve 31 of the present invention
  • the dashed line B indicates the characteristic of the fixed throttle 12
  • the broken line C indicates the characteristic of the conventional differential pressure detecting valve and the fixed throttle.
  • a fixed throttle has a fixed oil pressure Q of 351 / min when the engine speed is rated at 2000 rpm, and a differential pressure of around 15 bar (P 1 -P 2).
  • Q fixed oil pressure
  • P 1 -P 2 differential pressure
  • the differential pressure across the fixed throttle decreases as shown by the dashed line C.
  • the dashed line C For example, at around 1000 rpm in the idling region, when the engine speed is 2000 rpm, About 7.5 bar, half of
  • the fixed throttle 12 when the engine speed is at the rated speed of 2000 rpm, the fixed throttle 12 has a discharge oil amount Q of the fixed pump 11 of 35 1 / in and a differential pressure of about 25 bar (about 25 bar).
  • the opening area is set so that P1 ⁇ P2) occurs.
  • the differential pressure across the fixed throttle decreases as indicated by the dashed-dotted line B. In the vicinity of pm, it is about 12.5 bar, which is half that at 2000 rpm.
  • Pk is set to about 10 bar as described above
  • the relationship between the output pressure Pc of the differential pressure detection valve 31, the passing flow rate Q of the flow control throttle 6a, and the capacity of the hydraulic pump 1 is as described above.
  • the capacity of the pressure pump 1 can be controlled to be small, improving fine operability and reducing fuel consumption.
  • a pressure lower than the differential pressure before and after the fixed throttle 12 by the predetermined value Pk by the differential pressure detection valve 31 is guided to the load sensing valve 5 as a signal pressure, and the target differential pressure is set.
  • the pressure (signal pressure) P c lower by a predetermined value P k than the pressure difference before and after the fixed throttle 1 2 which is the output pressure of the differential pressure detection valve 3 1 has information on the engine rotation speed. Since the displacement of the hydraulic pump 1 can be controlled by linking to the engine speed, and the differential pressure before and after the fixed throttle 12 is used as the signal pressure Pc linked to the engine speed, the signal pressure P The c can be used with the mouth sensing valve 5 without modulating, and the structure of the load sensing valve 5 can be simplified.
  • the opening area of the fixed throttle 12 is smaller than the pressure difference before and after the fixed throttle 12 which is the output pressure of the differential pressure detection valve 3 1 at the rated rotation speed of the engine 9 by a predetermined value Pk.
  • the differential pressure across the fixed throttle 12 is set to be the same as the differential pressure across the conventional throttle, which uses the differential pressure across the constant throttle 12 as it is, and the rate of decrease in the differential pressure across the fixed throttle 12 relative to the engine speed.
  • the output pressure P c of the differential pressure detection valve 31 in the idle rotation region is obtained. Is smaller than the pressure difference before and after the conventional throttle, so that the capacity of the hydraulic pump 1 can be reduced in the idle rotation region where the amount of work is small, so that the fine operability can be improved and the fuel consumption can be reduced.
  • FIG. 3 is a circuit diagram of the valve device 50 of the present embodiment, in which the differential pressure detection valve 31 shows a state where the fixed pump 11 is at a neutral position when stopped.
  • FIG. 4A is a structural diagram of the valve device 50, and FIG. 4B shows the pressure receiving portions 31a, 31b, 31c of the differential pressure detecting valve 31.
  • the valve device 50 has a valve block 51, and the valve block 51 is connected to a pump port 52 connected to a discharge path 11a of the fixed pump 11 and a tank T.
  • the four ports of the load sensing port 55 connected to the signal oil passage 14 are formed in the order of ports 54, 52, 55, 53 from the left side in the figure.
  • a spool hole 56 is formed in the valve block 51, and a spool 57 is slidably inserted into the spool hole 56.
  • the spool 57 has a small-diameter portion 57a, a large-diameter portion 57b, and a shaft portion 57c between the two, and corresponds to the small-diameter portion 57a and the large-diameter portion 57b of the spool 57.
  • a small diameter portion 56a and a large diameter portion 56b are also formed in the spool hole 56.
  • an internal port 61 connected to the pump port 52 and an internal port 62 located outside the internal port 61 and connected to the actuator port 54 are formed in the small diameter portion 56a of the spool hole 56.
  • the large diameter portion 56b has an internal port 63 connected to the load sensing port 55, and an internal port 64 located outside the internal port 63 and connected to the tank port 53.
  • the inner ports 61, 64 on both sides are formed as a part of openings 65, 66 which open to the outer surface of the valve block 51, and these openings 65, 66 are plugs 6 respectively. Blocked at 7, 68.
  • a hollow portion 70 extending in the axial direction from the vicinity of the internal port 61 and opening at the small-diameter side end is formed in the small-diameter portion 57 a of the spool 57, and the opening at the distal end is closed by a spring guide 71.
  • the small-diameter portion 57a is provided with a radial throttle hole 72, which constitutes the above-mentioned fixed throttle 12, which communicates the internal port 61 with the hollow portion 70, and a hollow portion 70, which is an internal port.
  • An opening hole 73 communicating with 62 is formed.
  • a second notch 75 is formed on the shoulder portion of the large-diameter portion 57 b adjacent to the shaft portion 57 c as a variable throttle for reducing pressure, which controls communication between the load sensing port 55 and the tank port 53.
  • a piston chamber 81 is formed in the large-diameter portion 57b of the spool 57 so as to open at the large-diameter end, and the piston chamber 81 has a radial passage 82a and an axial passage 82b.
  • a piston 83 is slidably inserted into the piston chamber 81, and the back of the piston 83 is in contact with the plug 68.
  • the axial passage 82b is provided with a plug 85 having a throttle hole 84 constituting the throttle 35 described above.
  • the spool 57 has the above-described structure as shown in FIG. 4B.
  • Pressure receiving portions 3 la, 31 b, and 31 c are formed. That is, a pressure receiving portion 31a is formed on the end face of the piston chamber 81 facing the piston 83, the pressure of the pump port 52 is guided to the pressure receiving portion 31a, and the spool 57 is moved to the left (in the first notch 74).
  • a pressure-receiving portion 31b is formed at the end of the small-diameter portion 57a of the spool 57, and the pressure of the circuit port 54 is guided to the pressure-receiving portion 31b, and the spool 57 is moved rightward in the drawing.
  • the opening direction of the second notch 75, and the pressure receiving portion 31c is formed on the end surface of the large diameter portion 57b adjacent to the intermediate shaft portion 57c of the spool 57 due to the area difference from the end surface of the small diameter portion 57a.
  • the pressure of the load sensing port 55 is guided to the pressure receiving portion 31c, and urges the spool 57 rightward in the figure (in the opening direction of the second notch 75).
  • the pressure receiving areas of the pressure receiving sections 31a, 31 and 31c are all set to be the same.
  • the above-mentioned spring 31d is sandwiched between the plug 67 and the spring guide 71 to urge the spool 57 rightward in the figure. I have.
  • the pressure receiving portions 31 a 31 c and the panel 31 d selectively open the first notch 74 and the second notch 75, and apply a pressure P c lower by a predetermined value than the differential pressure across the throttle hole 72 (fixed throttle 12).
  • a spool urging means generated at the load sensing port 55 is configured.
  • the balance of the force of the spool 57 can be expressed by the following equation.
  • a s d Pressure receiving area of pressure receiving part 31a
  • a 1 s Pressure receiving area of pressure receiving part 31 c
  • the first notch 74 closes and the pressure oil does not flow into the load sensing port 55, and at the same time, the second notch 75 opens to release the pressure oil from the load sensing port 55 from the tank port 53. Drain to tank T and reduce pressure P c.
  • the pressure Pc decreases, the left side of the above equation (11) decreases, and the spool 57 starts to move leftward in the figure.
  • the first notch 74 opens and pressure oil flows into the load sensing port 55, and at the same time, the second notch 75 closes and discharges the pressure oil from the mouth sensing port 55. And the pressure P c recovers.
  • the fixed throttle 12 and the differential pressure detection valve 31 are configured as an integrated valve device using a common spool 57, the configuration of the fixed throttle 12 and the differential pressure detection valve 31 is simplified. Can be realized.
  • the fixed throttle 12 is composed of the radial throttle hole 72, no fluid force is generated in the throttle hole 72, and the flow rate through the throttle hole 72 changes due to a change in the engine rotation speed. Also, the stroke of the spool 57 is not affected by the fluid force, generates an accurate signal pressure linked to the engine speed, and improves control accuracy.
  • the output of the differential pressure detection valve 31 is directly introduced as the signal pressure to the pressure receiving portion 5c of the mouth sensing valve 5, but may be indirectly derived.
  • the signal pressure is detected by a pressure sensor and input to the controller.
  • a signal is output to the solenoid proportional valve and the output pressure of the solenoid proportional valve is received by the load sensing valve 5 You can lead to part 5c.
  • a process performed by the controller for example, there is a low-pass filter process (dead zone process) for avoiding the influence of a change in the engine speed due to a load change.
  • the pressure linked to the engine rotation speed can be used as it is as the set differential pressure of the load sensing valve, so that the structure of the load sensing valve can be simplified, and in the idle rotation region where the amount of work is small.
  • fine operability can be improved and fuel consumption can be reduced.
  • the differential pressure detecting means is configured as a valve device integrated with the throttle, the composite of the throttle and the differential pressure detecting means can be realized with a simplified configuration.
  • the throttle is formed with a small hole in the radial direction, the influence of the fluid force on the spool displacement can be avoided, and an accurate signal pressure linked to the engine speed can be generated.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne un dispositif de régulation du débit nominal d'une pompe et un dispositif à soupape. Un étranglement fixe (12) est formé sur un chemin d'alimentation (11) conduisant à une pompe fixe (11) entraînée en rotation par un moteur (9) qui entraîne également en rotation une pompe hydraulique (1). L'étranglement fixe (12) est associé à une soupape de détection (31) conçue pour détecter un différentiel de pression dans l'étranglement fixe (12) et délivrer une pression inférieure, d'une valeur spécifiée, audit différentiel de pression. Cette soupape de détection (31) du différentiel de pression délivre une sortie qui est transmise comme une pression signal à une partie (5c) conçue pour recevoir une valeur de pression d'une soupape de détection de charge (5), et un différentiel de pression cible est défini. Grâce aux dispositifs de cette invention, une pression associée à une vitesse de rotation du moteur peut être utilisée en tant que différentiel de pression d'ouverture de la soupape de détection de charge, la structure de la soupape de détection de charge peut ne pas être compliquée et le débit nominal de la pompe peut être réduit dans une zone de rotation au ralenti où la quantité de travail est faible de manière à accroître l'aptitude à la régulation permettant un réglage fin et une réduction de la consommation de carburant.
PCT/JP2000/003386 1999-05-28 2000-05-26 Dispositif de regulation du debit nominal d'une pompe et dispositif a soupape WO2000073664A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP00929873A EP1099856A1 (fr) 1999-05-28 2000-05-26 Dispositif de regulation du debit nominal d'une pompe et dispositif a soupape
KR10-2003-7002113A KR20030019921A (ko) 1999-05-28 2000-05-26 밸브 장치
KR1020007014513A KR20010053054A (ko) 1999-05-28 2000-05-26 펌프 용량 제어장치 및 밸브장치
US09/744,308 US6422009B1 (en) 1999-05-28 2000-05-26 Pump capacity control device and valve device
JP2001500127A JP3756814B2 (ja) 1999-05-28 2000-05-26 ポンプ容量制御装置及び弁装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP14960399 1999-05-28
JP11/149603 1999-05-28

Publications (1)

Publication Number Publication Date
WO2000073664A1 true WO2000073664A1 (fr) 2000-12-07

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PCT/JP2000/003386 WO2000073664A1 (fr) 1999-05-28 2000-05-26 Dispositif de regulation du debit nominal d'une pompe et dispositif a soupape

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US (1) US6422009B1 (fr)
EP (1) EP1099856A1 (fr)
JP (1) JP3756814B2 (fr)
KR (2) KR20030019921A (fr)
CN (1) CN1306606A (fr)
WO (1) WO2000073664A1 (fr)

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JP2015209866A (ja) * 2014-04-24 2015-11-24 株式会社不二越 油圧駆動装置
US20170089332A1 (en) * 2015-09-30 2017-03-30 Robert Bosch Gmbh Pump-Regulator Combination with Power Limitation
CN110621887A (zh) * 2017-06-16 2019-12-27 川崎重工业株式会社 油压系统
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JP2009174672A (ja) * 2008-01-28 2009-08-06 Nachi Fujikoshi Corp 油圧駆動装置
JP2015209866A (ja) * 2014-04-24 2015-11-24 株式会社不二越 油圧駆動装置
US20170089332A1 (en) * 2015-09-30 2017-03-30 Robert Bosch Gmbh Pump-Regulator Combination with Power Limitation
US10215170B2 (en) * 2015-09-30 2019-02-26 Robert Bosch Gmbh Pump-regulator combination with power limitation
CN110621887A (zh) * 2017-06-16 2019-12-27 川崎重工业株式会社 油压系统
US20220282457A1 (en) * 2019-09-25 2022-09-08 Hitachi Construction Machinery Tierra Co., Ltd. Construction Machine

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US6422009B1 (en) 2002-07-23
JP3756814B2 (ja) 2006-03-15
KR20030019921A (ko) 2003-03-07
EP1099856A1 (fr) 2001-05-16
KR20010053054A (ko) 2001-06-25
CN1306606A (zh) 2001-08-01

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